JP2007278625A - Expansion valve and air conditioner using it - Google Patents

Expansion valve and air conditioner using it Download PDF

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JP2007278625A
JP2007278625A JP2006106975A JP2006106975A JP2007278625A JP 2007278625 A JP2007278625 A JP 2007278625A JP 2006106975 A JP2006106975 A JP 2006106975A JP 2006106975 A JP2006106975 A JP 2006106975A JP 2007278625 A JP2007278625 A JP 2007278625A
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resonance
expansion valve
pipe
valve
valve body
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JP4079177B2 (en
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Toru Yukimoto
徹 雪本
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Daikin Industries Ltd
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Daikin Industries Ltd
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Priority to JP2006106975A priority Critical patent/JP4079177B2/en
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to CN2007800119165A priority patent/CN101416006B/en
Priority to US12/224,889 priority patent/US20090019871A1/en
Priority to AU2007236648A priority patent/AU2007236648B2/en
Priority to EP07741242A priority patent/EP2006617A4/en
Priority to KR1020087022885A priority patent/KR20080096838A/en
Priority to PCT/JP2007/057806 priority patent/WO2007116991A1/en
Publication of JP2007278625A publication Critical patent/JP2007278625A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Valves (AREA)
  • Temperature-Responsive Valves (AREA)
  • Lift Valve (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide an expansion valve and an air conditioner using it reducing noise due to acoustic resonance by providing adjustment of resonance characteristics of piping connected to a restriction part of the expansion valve and filled with a substantially liquid coolant. <P>SOLUTION: The expansion valve has a valve body 1, the restriction part 18 formed in a valve body 1 interior, two piping connection parts 11, 12 communicated with the front and rear of the restriction part 18, and at least one opening 30 exposing a coolant communication passage to an exterior of the valve body 1, wherein the coolant communication passage is connected to the restriction part from the piping connection part 12 to which the piping 19 filled with the substantially liquid coolant is connected. In the expansion valve 1, the valve body 1 is formed such that a resonance adjuster 31 provided with a resonance space for adjusting the resonance characteristics of the piping 19 filled with the substantially liquid coolant can be attached to an outer side of the valve body 1 in a state communicating with the opening 30. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、一般の冷凍サイクルに用いられ、高温高圧の冷媒を膨張させて低温低圧の冷媒にする膨張弁及びこれを用いた空気調和機に関する。   The present invention relates to an expansion valve that is used in a general refrigeration cycle, expands a high-temperature and high-pressure refrigerant to form a low-temperature and low-pressure refrigerant, and an air conditioner using the expansion valve.

従来空気調和装置において騒音の低下が望まれており、特に、膨張弁における低騒音化が必要とされている。また、この膨張弁における騒音問題としては、主として、膨張弁の上流側の冷媒流通抵抗の増加や、凝縮器の能力不足など要因で膨張弁に流入する冷媒流が気液二相流になった場合の騒音に着目されていた。この騒音の発生メカニズムは、密度の異なる冷媒が不規則に膨張弁の弁本体の内部を通過することにより、膨張弁内部における圧力の変動が激しくなり、圧力変動が膨張弁を形成するケースに伝播する。そして、膨張弁の圧力変動により弁体自体が加振され、その振動がシャフトを通してロータに伝わり、ケースを振動させるというものであった。   Conventionally, a reduction in noise is desired in an air conditioner, and in particular, a reduction in noise in an expansion valve is required. In addition, as a noise problem in this expansion valve, the refrigerant flow flowing into the expansion valve has become a gas-liquid two-phase flow mainly due to factors such as an increase in refrigerant flow resistance upstream of the expansion valve and insufficient capacity of the condenser. Attention was paid to the noise of the case. This noise generation mechanism is caused by the fact that refrigerants with different densities irregularly pass through the inside of the valve body of the expansion valve, so that the pressure fluctuation in the expansion valve becomes intense, and the pressure fluctuation propagates to the case forming the expansion valve. To do. Then, the valve body itself is vibrated by the pressure fluctuation of the expansion valve, the vibration is transmitted to the rotor through the shaft, and the case is vibrated.

このような問題に対し、特許文献１では、膨張弁の弁本体の筺体に弁本体の内部に連通する中空形状の空間を筐体内に形成したものが提案されている。これは、筺体内に形成された中空形状の空間における圧力変動の周波数特性と、膨張弁の弁本体内部における圧力減圧時の圧力変動による周波数特性とを干渉させることにより、不快と感じられる周波数の騒音レベルを下げるものである。また、特許文献２には、膨張弁内において、膨張弁の出入口を形成する二つの配管と絞り部との間それぞれに膨張室を設けたものが提案されている。この膨張弁は、冷媒がこの２つの膨張室を通過するときに、冷媒の圧力脈動を段階的に減衰することにより、冷媒通過音を低減するものであり、二つの膨張室を消音器として機能させたものである。また、特許文献３では、マルチエアコンにおいて、負荷変動に対応するために一部の空気調和機の膨張弁が弁開度調整されたときに、他室の空気調和機の膨張弁の入口側において過渡的に気液二相流状態となり、圧力脈動が生ずる場合の騒音対策として、弁体、弁座、接続管の外周周りなどの膨張弁の構成部品内に消音器を設けたものが提案されている。この消音器は、容積の閉じた空間室とそれに連通する所定長さと断面積の直管とからなるものであって、ヘルムホルツ型共鳴器と近似した構成のものである。
特開平１０−１６０２９０号公報 特開平１１−３２５６５８号公報 特開平８−１３５８４２号公報 In order to solve such a problem, Patent Document 1 proposes a case in which a hollow space communicating with the inside of a valve body is formed in a housing of a valve body of an expansion valve. This is because the frequency characteristic of the pressure fluctuation in the hollow space formed in the housing interferes with the frequency characteristic due to the pressure fluctuation at the time of pressure reduction inside the valve body of the expansion valve, so that the frequency which is felt uncomfortable. It reduces the noise level. Patent Document 2 proposes an expansion valve in which an expansion chamber is provided between two pipes that form an inlet / outlet of the expansion valve and a throttle portion. This expansion valve reduces the refrigerant passing sound by gradually reducing the pressure pulsation of the refrigerant when the refrigerant passes through the two expansion chambers, and functions as two silencers. It has been made. Moreover, in patent document 3, in the multi air conditioner, when the opening degree of the expansion valve of some of the air conditioners is adjusted to cope with load fluctuations, the inlet side of the expansion valve of the air conditioner in the other room As a countermeasure against noise when a gas-liquid two-phase flow condition occurs transiently and pressure pulsation occurs, it has been proposed to provide a silencer in the expansion valve components such as the valve body, valve seat, and the periphery of the connecting pipe. ing. This silencer is composed of a space chamber having a closed volume and a straight pipe having a predetermined length and a cross-sectional area communicating with the space chamber, and has a configuration similar to a Helmholtz resonator.
JP-A-10-160290 Japanese Patent Laid-Open No. 11-325658 JP-A-8-135842

ところが、発明者の研究により、膨張弁の騒音発生は上記のような場合ばかりでなく、膨張弁の絞り部に接続され、かつ、略液冷媒で満たされる配管については、配管内の音響共鳴により冷媒音が悪化する場合のあることが解明された。絞り部に接続される配管であり、かつ略液冷媒で満たされる配管としては、通常の運転における膨張弁の上流側配管がこれに相当する。また、絞り部に接続され、かつ、略液冷媒で満たされる配管としては、このような膨張弁の上流側配管のみならず、下流側配管がこれに相当する場合もある。例えば、マルチエアコンにおける暖房運転時においては、室内ユニットに設けられる室内膨張弁の上流側配管及び下流側配管の何れもがこれに相当する。   However, according to the inventor's research, the noise generation of the expansion valve is not only in the above case, but the pipe connected to the throttle portion of the expansion valve and filled with the substantially liquid refrigerant is caused by acoustic resonance in the pipe. It has been clarified that the refrigerant sound may deteriorate. The pipe connected to the throttle portion and filled with the substantially liquid refrigerant corresponds to the upstream pipe of the expansion valve in normal operation. Further, the pipe connected to the throttle portion and filled with the substantially liquid refrigerant may correspond to not only the upstream pipe of the expansion valve but also the downstream pipe. For example, at the time of heating operation in a multi air conditioner, both the upstream side piping and the downstream side piping of the indoor expansion valve provided in the indoor unit correspond to this.

ここで、このマルチエアコンにおいて、どの配管が絞り部に接続され、かつ、略液冷媒で満たされる配管に相当するかについて説明する。
図８は一般的なヒートポンプ式マルチエアコンにおける冷媒回路を示す。この冷媒回路は、圧縮機１０１、四路切換弁１０２、室外側熱交換器１０３、室外膨張弁１０４、受液器１０５などを収納した１台の室外ユニット１０６に対し、室内膨張弁１０７、室内側熱交換器１０８を収納した複数台（図では２台の場合を例示）の室内ユニット１０９が接続されている。この空気調和機においては、冷房運転時、四路切換弁１０２の切換により、実線矢印のように、圧縮機１０１、四路切換弁１０２、室外側熱交換器１０３、暖房用の膨張弁、受液器１０５、室内膨張弁１０７、室内側熱交換器１０８、四路切換弁１０２、圧縮機１０１の経路で冷媒が流通する冷媒回路が形成される。なお、室内ユニット１０９に組み込まれている室内膨張弁１０７、室内側熱交換器１０８の回路部分は各室並列に接続されている。そして、この冷房運転時においては、室外膨張弁１０４及び室内膨張弁１０７で冷媒制御して、室外側熱交換器１０３を凝縮器として作用させ、室内側熱交換器１０８を蒸発器として作用させている。このような冷媒回路が形成されることにより、室内空気が室内側熱交換器１０８で冷却除湿される。この冷媒回路においては、運転条件が定格冷房運転条件に近い状態の場合には、室内膨張弁１０７の上流側配管が、前述の絞り部に接続され、かつ、略液冷媒で満たされる配管に該当する。また、この冷媒回路の運転における室内膨張弁１０７の上流側配管で、配管内の音響共鳴により冷媒音の悪化する場合のあることが発明者により解明された。 Here, in this multi air conditioner, which pipe is connected to the throttle portion and corresponds to a pipe that is substantially filled with liquid refrigerant will be described.
FIG. 8 shows a refrigerant circuit in a general heat pump type multi air conditioner. This refrigerant circuit includes an indoor expansion valve 107, a chamber for a single outdoor unit 106 that houses a compressor 101, a four-way switching valve 102, an outdoor heat exchanger 103, an outdoor expansion valve 104, a liquid receiver 105, and the like. A plurality of indoor units 109 (two cases are illustrated in the figure as examples) housing the inner heat exchanger 108 are connected. In this air conditioner, during the cooling operation, by switching the four-way switching valve 102, the compressor 101, the four-way switching valve 102, the outdoor heat exchanger 103, the heating expansion valve, the receiving valve, as indicated by solid arrows. A refrigerant circuit is formed in which refrigerant flows through the path of the liquid device 105, the indoor expansion valve 107, the indoor side heat exchanger 108, the four-way switching valve 102, and the compressor 101. Note that the circuit portions of the indoor expansion valve 107 and the indoor heat exchanger 108 incorporated in the indoor unit 109 are connected in parallel in each chamber. During this cooling operation, the outdoor expansion valve 104 and the indoor expansion valve 107 control the refrigerant so that the outdoor heat exchanger 103 acts as a condenser and the indoor heat exchanger 108 acts as an evaporator. Yes. By forming such a refrigerant circuit, the indoor air is cooled and dehumidified by the indoor heat exchanger 108. In this refrigerant circuit, when the operation condition is close to the rated cooling operation condition, the upstream pipe of the indoor expansion valve 107 corresponds to a pipe that is connected to the aforementioned throttle part and is substantially filled with liquid refrigerant. To do. Further, it has been clarified by the inventor that the refrigerant sound may be deteriorated by the acoustic resonance in the pipe in the upstream pipe of the indoor expansion valve 107 in the operation of the refrigerant circuit.

一方、暖房運転時は、四路切換弁１０２の切り換えにより、破線矢印のように、圧縮機１０１、四路切換弁１０２、室内側熱交換器１０８、室内膨張弁１０７、受液器１０５、室外膨張弁１０４、室外側熱交換器１０３、四路切換弁１０２、圧縮機１０１の経路で冷媒が流通する冷媒回路が形成される。この場合においても、各室内ユニット１０９に収納されている室内側熱交換器１０８、室内膨張弁１０７の回路部分は並列に接続されている。そして、この暖房運転時においては、室外膨張弁１０４及び室内膨張弁１０７で冷媒制御して、室外側熱交換器１０３を蒸発器として作用させ、室内側熱交換器１０８を凝縮器として作用させている。このような冷媒回路が形成されることにより、室内空気が室内側熱交換器１０８で加熱される。この冷媒回路においては、運転条件が定格暖房運転条件に近い状態の場合には、室外膨張弁１０４の上流側配管が、前述の絞り部に接続され、かつ、略液冷媒で満たされる配管に該当する。また、この冷媒回路の運転における室外膨張弁１０４の上流側配管で、配管内の音響共鳴により冷媒音が悪化する場合のあることが発明者により解明された。   On the other hand, during the heating operation, by switching the four-way switching valve 102, the compressor 101, the four-way switching valve 102, the indoor heat exchanger 108, the indoor expansion valve 107, the liquid receiver 105, the outdoor, as indicated by the broken line arrows. A refrigerant circuit is formed in which refrigerant flows through the expansion valve 104, the outdoor heat exchanger 103, the four-way switching valve 102, and the compressor 101. Even in this case, the circuit portions of the indoor heat exchanger 108 and the indoor expansion valve 107 housed in each indoor unit 109 are connected in parallel. During this heating operation, the refrigerant is controlled by the outdoor expansion valve 104 and the indoor expansion valve 107 so that the outdoor heat exchanger 103 acts as an evaporator and the indoor heat exchanger 108 acts as a condenser. Yes. By forming such a refrigerant circuit, indoor air is heated by the indoor heat exchanger 108. In this refrigerant circuit, when the operation condition is close to the rated heating operation condition, the upstream pipe of the outdoor expansion valve 104 corresponds to a pipe that is connected to the above-mentioned throttle part and is substantially filled with liquid refrigerant. To do. Further, it has been clarified by the inventor that the refrigerant sound may be deteriorated by the acoustic resonance in the pipe in the upstream pipe of the outdoor expansion valve 104 in the operation of the refrigerant circuit.

このような冷媒回路において、一部の室内ユニット１０９を停止させる場合、この室内ユニット１０９の室内側熱交換器１０８は高圧回路中に連通されている。このため、室内側熱交換器１０８の出口側に位置する室内膨張弁１０７を全閉にして長時間運転停止する場合は、高圧ガス冷媒がこの運転停止中の室内側熱交換器１０８で凝縮液化して貯留される。室内側熱交換器１０８に冷媒が凝縮液化して貯留されると、冷媒回路内の冷媒量が不足し、正常な圧力で運転できなくなり、暖房運転に支障をきたすことがあり得る。そこで、これを回避するために、暖房運転停止中の室内ユニット１０９内の室内膨張弁１０７は、全閉でなく小開度にして、液冷媒を絶えず少量流通させることにより液冷媒の滞留を抑制するようにしている。この状態では、膨張弁の上流側配管が液冷媒で満たされることは言うに及ばず、下流側配管も液冷媒で満たされる。したがって、この冷媒回路における室内膨張弁１０７の上流側配管及び下流側配管は、前述の絞り部に接続され、かつ、略液冷媒で満たされる配管に該当する。また、この冷媒回路の運転における室内膨張弁１０７の上流側配管及び下流側配管で、配管内の音響共鳴により冷媒音が悪化する場合のあることが発明者により解明された。   In such a refrigerant circuit, when some indoor units 109 are stopped, the indoor heat exchanger 108 of the indoor unit 109 is communicated with the high-pressure circuit. Therefore, when the indoor expansion valve 107 located on the outlet side of the indoor heat exchanger 108 is fully closed and the operation is stopped for a long time, the high-pressure gas refrigerant is condensed and liquefied in the indoor heat exchanger 108 when the operation is stopped. And stored. If the refrigerant is condensed and stored in the indoor heat exchanger 108, the amount of refrigerant in the refrigerant circuit becomes insufficient, and the operation cannot be performed at normal pressure, which may hinder the heating operation. Therefore, in order to avoid this, the indoor expansion valve 107 in the indoor unit 109 in the heating operation stop is not fully closed, but has a small opening, and the liquid refrigerant is constantly circulated in a small amount to suppress the retention of the liquid refrigerant. Like to do. In this state, it goes without saying that the upstream piping of the expansion valve is filled with liquid refrigerant, and the downstream piping is also filled with liquid refrigerant. Therefore, the upstream side piping and the downstream side piping of the indoor expansion valve 107 in this refrigerant circuit correspond to piping connected to the above-described throttle part and filled with substantially liquid refrigerant. Further, the inventor has clarified that the refrigerant noise may be deteriorated by the acoustic resonance in the pipe in the upstream pipe and the downstream pipe of the indoor expansion valve 107 in the operation of the refrigerant circuit.

このような絞り部に接続され、かつ、略液冷媒で満たされる配管においては、図９に示すような共鳴空間が想定される。図９は、膨張弁１１０の絞り部１１１に接続され、かつ、略液冷媒で満たされる配管１１２が接続された配置例であり、この配管１１２にはフィルタ１１３が接続されている。この場合における配管の共鳴空間では、膨張弁１１０の弁室１１４の側壁１１４ａが閉端として作用し、配管接続部に接続されている配管１１２におけるフィルタ１１３の大口径部１１３ａが開放端とし作用する共鳴モードの生じる場合がある。共鳴モードは、図９にも図示されるように、閉端位置では振幅が最大となり（所謂腹となり）、開放端位置では振幅が０となる（所謂節となる）。一方、膨張弁１１０における騒音の発信源は絞り部１１１付近の冷媒の乱れによると考えられるが、この絞り部１１１が上記共鳴モードの腹の位置に存在するため加振されやすい。したがって、絞り部１１１を通過する高速冷媒のエネルギが加えられて共鳴モードが励起されやすい。   A resonance space as shown in FIG. 9 is assumed in a pipe connected to such a throttle portion and filled with a substantially liquid refrigerant. FIG. 9 shows an arrangement example in which a pipe 112 connected to the throttle portion 111 of the expansion valve 110 and substantially filled with a liquid refrigerant is connected. A filter 113 is connected to the pipe 112. In the piping resonance space in this case, the side wall 114a of the valve chamber 114 of the expansion valve 110 acts as a closed end, and the large-diameter portion 113a of the filter 113 in the piping 112 connected to the piping connection portion acts as an open end. A resonance mode may occur. As shown in FIG. 9, the resonance mode has a maximum amplitude at the closed end position (so-called antinode) and 0 at the open end position (so-called node). On the other hand, the source of noise in the expansion valve 110 is considered to be due to the disturbance of the refrigerant in the vicinity of the throttle portion 111. However, since the throttle portion 111 exists at the antinode position of the resonance mode, it is easy to be excited. Accordingly, the energy of the high-speed refrigerant passing through the throttle unit 111 is added and the resonance mode is easily excited.

図１０に、振幅の大小のイメージを破線で示した共鳴モードの模式図を示すが、前述の絞り部１１１に接続されるとともに略液冷媒で満たされる配管１１２では、図９又は図１０（ａ）のような１次モードだけでなく、図１０（ｂ）、（ｃ）に示すような２次、３次…のようなあらゆる共鳴モードが励起されやすい。そこで、発明者は、絞り部１１１の位置を変えることはできないが、共鳴空間の共鳴特性を調整、特に、共鳴モードの腹の位置を移動させる調整により、音響共鳴における振幅レベルを低減させ得ることを見出した。また、実機における共鳴モードは、膨張弁に接続される部品、例えば、フィルタ、消音器、熱交換器などあらゆる断面積変化部の特性や、流通する冷媒の状態などによって決まるため、共鳴特性は空気調和機のシステム設計に依存することが分かってきた。すなわち、共鳴特性の調整は空気調和機のシステム設計により異なることが発明者により解明された。   FIG. 10 is a schematic diagram of a resonance mode in which an image of amplitude is indicated by a broken line. In the pipe 112 connected to the above-described throttle portion 111 and filled with substantially liquid refrigerant, FIG. 9 or FIG. ) As well as all resonance modes such as secondary, tertiary, etc. as shown in FIGS. 10B and 10C are easily excited. Therefore, the inventor cannot change the position of the diaphragm 111, but can adjust the resonance characteristics of the resonance space, in particular, the amplitude level in the acoustic resonance can be reduced by moving the antinode of the resonance mode. I found. In addition, the resonance mode in an actual machine is determined by the characteristics of all cross-sectional area changing parts such as components connected to the expansion valve, such as filters, silencers, and heat exchangers, and the state of the circulating refrigerant. It has been found that it depends on the system design of the harmonic machine. That is, the inventors have clarified that the adjustment of the resonance characteristics varies depending on the system design of the air conditioner.

ところで、前述の従来の膨張弁の騒音対策は、膨張弁上流側の気液二相流による圧力変動による騒音に着目したものであり、このような音響共鳴に起因する騒音に着目したものではない。また、音響共鳴に起因する騒音に着目したものは、未だ発表されていない。なお、前述の各特許文献に記載されている騒音対策は、絞り部の近傍に消音器を設けているので、音響共鳴に影響を与えることはできるが、もともと音響共鳴に着目したものではなく、共鳴特性の調整を考えたものではない。したがって、共鳴特性の調整は、空気調和機のシステム設計に依存する点についてもなんら示唆したものではない。   By the way, the above-described conventional noise countermeasures for the expansion valve pay attention to noise due to pressure fluctuation due to gas-liquid two-phase flow upstream of the expansion valve, and do not pay attention to noise caused by such acoustic resonance. . In addition, no attention has been paid to noise due to acoustic resonance. In addition, since the noise countermeasures described in each of the above-mentioned patent documents are provided with a silencer in the vicinity of the diaphragm portion, they can affect the acoustic resonance, but are not originally focused on the acoustic resonance, It is not intended to adjust the resonance characteristics. Therefore, there is no suggestion that the adjustment of the resonance characteristics depends on the system design of the air conditioner.

本発明は、従来技術に存在するこのような問題点に着目してなされたものであって、絞り部に接続され、かつ、略液冷媒で満たされる配管の共鳴特性を調整可能とすることにより、音響共鳴による騒音を低減する膨張弁及びこの膨張弁を用いた空気調和機を提供することを目的とする。   The present invention has been made paying attention to such a problem existing in the prior art, and by making it possible to adjust the resonance characteristics of the pipe connected to the throttle portion and filled with substantially liquid refrigerant. An object of the present invention is to provide an expansion valve that reduces noise due to acoustic resonance and an air conditioner using the expansion valve.

上記課題を解決する本発明に係る膨張弁は、弁本体と、弁本体内部に形成される絞り部と、この絞り部の前後に連通する二つの配管接続部と、略液冷媒で満たされる配管が接続される配管接続部から絞り部に至る冷媒流通路を弁本体の外部に開放する少なくとも一つの開口部とを有する。そして、前記弁本体は、略液冷媒で満たされる配管の共鳴特性を調整する共鳴空間を備えた共鳴調整器を、前記開口部に連通する態様で弁本体の外側に取り付け可能に形成されている。このように構成された膨張弁を用いて空気調和機のシステム設計を行えば、この空気調和機における膨張弁の絞り部に接続され、かつ、略液冷媒で満たされる配管の共鳴特性に対応した共鳴調整器を、膨張弁の弁本体外部に取り付けすることができる。これにより、共鳴モードの腹の位置を調整することができ、共鳴音の振幅レベルを低減して、騒音を低減することができる。   An expansion valve according to the present invention that solves the above problems includes a valve body, a throttle portion formed inside the valve body, two pipe connection portions communicating before and after the throttle portion, and a pipe filled with substantially liquid refrigerant. And at least one opening that opens a refrigerant flow path from the pipe connection to the throttle to the outside of the valve body. And the said valve main body is formed so that the resonance regulator provided with the resonance space which adjusts the resonance characteristic of piping filled with substantially liquid refrigerant can be attached to the outer side of the valve main body in the aspect connected to the said opening part. . If the system design of the air conditioner is performed using the expansion valve configured as described above, it corresponds to the resonance characteristic of the pipe connected to the throttle portion of the expansion valve in the air conditioner and filled with substantially liquid refrigerant. A resonance regulator can be attached outside the valve body of the expansion valve. Thereby, the antinode position of the resonance mode can be adjusted, the amplitude level of the resonance sound can be reduced, and the noise can be reduced.

また、本発明に係る膨張弁は、弁本体の外部に共鳴調整器を取り付けたものでもよい。この発明の場合、共鳴調整器が膨張弁の外部に取り付けられているため、取り付けスペースに自由度があり空気調和機のシステム設計に対応したものを装備させることができる。また、空気調和機のシステムにより共鳴特性が異なることに対応するには、弁本体及び弁駆動部を変更せずに共鳴調整器のみを変更するだけでよいので、膨張弁の共用化を行うことができる。   Further, the expansion valve according to the present invention may be one in which a resonance regulator is attached to the outside of the valve body. In the case of this invention, since the resonance adjuster is attached to the outside of the expansion valve, it is possible to equip the attachment space with a degree of freedom and corresponding to the system design of the air conditioner. Also, in order to cope with the difference in resonance characteristics depending on the air conditioner system, it is only necessary to change the resonance adjuster without changing the valve body and the valve drive unit. Can do.

また、前記開口部を複数個設け、これら開口部に連通するように複数の共鳴調整器を弁本体の外側に取り付けるようにすることもできる。膨張弁の絞り部に接続され、かつ、略液冷媒で満たされる配管には、前述のように１個の共鳴空間が形成されるだけではなしに複数の共鳴空間が形成されることがある。例えば、この配管に大口径のフィルタと受液器が直列に接続されているような場合、フィルタを開放端とする共鳴空間と、受液器を開放端とする共鳴空間とが形成され得る。このような場合、複数の共鳴調整器を取り付けることにより、個々の共鳴空間毎の共鳴特性を個々の共鳴調整器で調整することができる。   Further, a plurality of the openings may be provided, and a plurality of resonance adjusters may be attached to the outside of the valve body so as to communicate with the openings. In the pipe connected to the throttle portion of the expansion valve and substantially filled with the liquid refrigerant, a plurality of resonance spaces may be formed in addition to the formation of one resonance space as described above. For example, when a large-diameter filter and a liquid receiver are connected in series to this pipe, a resonance space with the filter as an open end and a resonance space with the liquid receiver as an open end can be formed. In such a case, by attaching a plurality of resonance adjusters, the resonance characteristics for each resonance space can be adjusted by each resonance adjuster.

また、共鳴調整器を、管状容器とすることもできるし、共鳴器形状の容器とすることもできる。
また、この共鳴調整器の内部に音波を反射しにくい部材を取り付けることもできる。共鳴音は反射されるので、音波を反射しにくい部材を取り付けることにより、共鳴音を低減することが可能となる。また、このような材料として、取り扱いの容易な多孔質体を用いることもできる。 In addition, the resonance adjuster can be a tubular container or a resonator-shaped container.
In addition, a member that hardly reflects sound waves can be attached inside the resonance adjuster. Since the resonance sound is reflected, it is possible to reduce the resonance sound by attaching a member that hardly reflects the sound wave. In addition, a porous body that can be easily handled can be used as such a material.

本発明に係る膨張弁によれば、絞り部に接続され、かつ、略液冷媒で満たされる配管の共鳴特性に対応した共鳴調整器を、膨張弁の弁本体の外部に取り付けすることができる。これにより、共鳴モードの腹の位置を調整することができ、共鳴音の振幅レベルを低減して、騒音を低減することができる。   According to the expansion valve according to the present invention, the resonance regulator corresponding to the resonance characteristic of the pipe connected to the throttle portion and substantially filled with the liquid refrigerant can be attached to the outside of the valve body of the expansion valve. Thereby, the antinode position of the resonance mode can be adjusted, the amplitude level of the resonance sound can be reduced, and the noise can be reduced.

以下、本発明の各実施の形態に係る膨張弁について、図面に基づき説明する。なお、各実施の形態に共通する要素には同一の符号を付し、重複説明を回避する。
（実施の形態１）
以下、この発明の実施の形態１に係る膨張弁について、図１に基づき説明する。図１は実施の形態１に係る膨張弁の縦断面図である。本実施の形態に係る膨張弁は、図１に示すように、弁本体１と、弁本体１の上部に取り付けられた弁駆動部２からなる。 Hereinafter, the expansion valve according to each embodiment of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the element common to each embodiment, and duplication description is avoided.
(Embodiment 1)
Hereinafter, an expansion valve according to Embodiment 1 of the present invention will be described with reference to FIG. 1 is a longitudinal sectional view of an expansion valve according to Embodiment 1. FIG. As shown in FIG. 1, the expansion valve according to the present embodiment includes a valve body 1 and a valve drive unit 2 attached to the upper part of the valve body 1.

弁本体１は、側面及び下面それぞれに配管接続部１１、１２を有し、両配管接続部１１、１２間に冷媒流通路が形成されている、この冷媒流通路は、弁座１３により仕切られ、上部に弁室１４が形成されている。弁座１３には弁孔１５が形成され、この弁孔１５に対し上方から弁棒１６の先端に形成されたニードル弁１７が進退自在に駆動されるように構成されている。そして、このニードル弁１７と弁座１３とにより絞り部１８が形成されている。なお、前記配管接続部１１、１２は、膨張弁に接続される配管１９の接続を容易にするために継手用配管により構成されている。   The valve body 1 has pipe connection portions 11 and 12 on the side surface and the lower surface, respectively, and a refrigerant flow passage is formed between the pipe connection portions 11 and 12. The refrigerant flow passage is partitioned by a valve seat 13. A valve chamber 14 is formed in the upper part. A valve hole 15 is formed in the valve seat 13, and a needle valve 17 formed at the tip of the valve rod 16 from above is configured to be driven to move forward and backward. The needle valve 17 and the valve seat 13 form a throttle portion 18. In addition, the said piping connection parts 11 and 12 are comprised by the piping for joints in order to make the connection of the piping 19 connected to an expansion valve easy.

弁駆動部２は、弁棒１６を上下動させるための駆動部であって、弁棒１６を連結するロータ２１、ロータ２１を囲うロータケース２２、ロータケース２２の外側に取り付けられたステータ２３などから構成されている。以上の構成は、膨張弁として従来公知の一般的な構成である。   The valve driving unit 2 is a driving unit for moving the valve rod 16 up and down, and includes a rotor 21 that connects the valve rod 16, a rotor case 22 that surrounds the rotor 21, a stator 23 that is attached to the outside of the rotor case 22, and the like. It is composed of The above configuration is a general configuration conventionally known as an expansion valve.

本実施の形態に係る膨張弁は、このような構成において、弁本体１における弁室１４の側方であって、側方の配管接続部１１に対向する位置に、弁室１４を外部に開口する開口部３０が設けられている。この開口部３０の大きさは、配管接続部１１に接続される配管１９の内径と略同一直径の円形孔に形成されている。また、弁本体１の外側には、前記配管１９と同一直径の管状の共鳴調整器３１を取り付け可能とするために、ソケット部３２が形成されている。   In such an arrangement, the expansion valve according to the present embodiment opens the valve chamber 14 to the outside at a position on the side of the valve chamber 14 in the valve body 1 and facing the side pipe connection portion 11. An opening 30 is provided. The size of the opening 30 is a circular hole having substantially the same diameter as the inner diameter of the pipe 19 connected to the pipe connection part 11. Further, a socket portion 32 is formed outside the valve body 1 so that a tubular resonance regulator 31 having the same diameter as the pipe 19 can be attached.

共鳴調整器３１は、配管１９と略同一直径の管状容器からなるものであり、その一端を開放し、他端を閉鎖したものである。そして、この管状容器からなる共鳴調整器３１は、開口部３０と同心状にソケット部３２にろう付けされて取り付けられている。   The resonance adjuster 31 is composed of a tubular container having substantially the same diameter as the pipe 19 and has one end opened and the other end closed. The resonance adjuster 31 including the tubular container is brazed and attached to the socket portion 32 concentrically with the opening 30.

このような共鳴調整器３１が弁本体１の外側に取り付けられると、図１に示すように、開放端は配管１９に取り付けられたフィルタ３５の大口径部３５ａであり、閉端は、弁本体１の外側に取り付けられ共鳴調整器３１の閉鎖された側の端部３１ａとする。これにより、共鳴空間が弁室１４の外側にはみ出して形成される。この結果、図１における１次共鳴モードを破線で示すように共鳴モードの腹及び節が調整される。このように共鳴特性が調整されると、絞り部１８で発生する加振エネルギは、共鳴モードの腹からずれた個所で加えられることになる。   When such a resonance regulator 31 is attached to the outside of the valve body 1, as shown in FIG. 1, the open end is a large-diameter portion 35a of the filter 35 attached to the pipe 19, and the closed end is the valve body. 1 is an end 31a on the closed side of the resonance adjuster 31 that is attached to the outside of 1. As a result, a resonance space is formed so as to protrude outside the valve chamber 14. As a result, the antinodes and nodes of the resonance mode are adjusted so that the primary resonance mode in FIG. When the resonance characteristics are adjusted in this way, the excitation energy generated in the diaphragm 18 is applied at a location deviated from the resonance mode antinode.

開口部３０に連通する共鳴調整器３１の取付位置は、配管１９の共鳴空間については絞り部の手前である必要があり、絞り部１８にできるだけ近いことが好ましい。このような共鳴調整器は、エネルギ吸収効果もあるので、エネルギ発生源に近いところに位置させることが好ましい。共鳴調整器３１は、このようなことから弁室１４の側面に設けられているが、その位置は配管接続部１１に対向する位置でなくてもよく、配管接続部１１の軸線に対し角度が付く位置に設けられてもよい。   The attachment position of the resonance adjuster 31 that communicates with the opening 30 needs to be in front of the restricting portion with respect to the resonance space of the pipe 19 and is preferably as close as possible to the restricting portion 18. Since such a resonance adjuster also has an energy absorption effect, it is preferable that the resonance adjuster be positioned near the energy generation source. For this reason, the resonance adjuster 31 is provided on the side surface of the valve chamber 14. You may provide in the position which attaches.

実施の形態１の膨張弁は、上記のように構成された膨張弁であって、共鳴調整器３１が取り付けられた膨張弁と、共鳴調整器３１が取り付けられていない膨張弁との実施の形態として例示されるものである。また、このように構成された共鳴調整器３１の取り付けられていない状態の膨張弁によれば、膨張弁の絞り部１８に接続され、かつ、略液冷媒で満たされる配管１９からなる共鳴空間の共鳴特性に対応した共鳴調整器３１を、膨張弁の弁本体１の外部に取り付けすることができる。これにより、共鳴モードの腹の位置を調整することができ、共鳴音の振幅レベルを低減して、騒音を低減することができる。また、このように共鳴調整器３１が取り付けられていない膨張弁の場合は、空気調和機のシステム設計者が各自で定める最適特性の共鳴調整器３１を自由に選択して膨張弁に取り付けることができる。   The expansion valve according to the first embodiment is an expansion valve configured as described above, and includes an expansion valve to which the resonance regulator 31 is attached and an expansion valve to which the resonance regulator 31 is not attached. It is illustrated as. Moreover, according to the expansion valve in the state where the resonance adjuster 31 thus configured is not attached, the resonance space composed of the pipe 19 connected to the throttle portion 18 of the expansion valve and filled with substantially liquid refrigerant. A resonance adjuster 31 corresponding to the resonance characteristics can be attached to the outside of the valve body 1 of the expansion valve. Thereby, the antinode position of the resonance mode can be adjusted, the amplitude level of the resonance sound can be reduced, and the noise can be reduced. Further, in the case of an expansion valve to which the resonance adjuster 31 is not attached in this way, the system designer of the air conditioner can freely select and attach the resonance adjuster 31 having the optimum characteristics determined by himself / herself to the expansion valve. it can.

また、共鳴調整器３１の取り付けられた状態の膨張弁の場合は、空気調和機のシステム設計に際し、予め配管１９からなる共鳴空間の共鳴特性に対応する共鳴調整器３１の取り付けられた膨張弁を用意すればよい。このようにして、共鳴特性を調整し得る膨張弁を空気調和機のシステムに採用することにより、共鳴モードの腹の位置を調整することができ、共鳴音の振幅レベルを低減して、騒音を低減することができる。   In the case of the expansion valve with the resonance adjuster 31 attached, the expansion valve with the resonance adjuster 31 attached corresponding to the resonance characteristic of the resonance space formed by the pipe 19 in advance is designed in designing the air conditioner system. Just prepare. In this way, by adopting an expansion valve that can adjust the resonance characteristics in the air conditioner system, the position of the antinode of the resonance mode can be adjusted, and the amplitude level of the resonance sound can be reduced to reduce noise. Can be reduced.

（実施の形態２）
実施の形態２に係る膨張弁は、図２に示すように、実施の形態１における膨張弁の共鳴調整器の直径を、配管１９の直径よりも細くした共鳴調整器４１を用いたものである。この場合の共鳴空間の閉端は、弁本体１の外側に取り付けられた共鳴調整器４１の閉鎖された側の端部４１ａとなる。実施の形態２の共鳴調整器４１の基本的な考え方は実施の形態１の共鳴調整器３１と同一であり、共鳴調整器４１の長さや直径を調整することにより、共鳴特性を調整することができ、音響共鳴による騒音の振幅レベルを下げて、共鳴音を低減することができる。 (Embodiment 2)
As shown in FIG. 2, the expansion valve according to the second embodiment uses a resonance regulator 41 in which the diameter of the resonance regulator of the expansion valve in the first embodiment is smaller than the diameter of the pipe 19. . In this case, the closed end of the resonance space is an end 41a on the closed side of the resonance adjuster 41 attached to the outside of the valve body 1. The basic concept of the resonance adjuster 41 of the second embodiment is the same as that of the resonance adjuster 31 of the first embodiment, and the resonance characteristics can be adjusted by adjusting the length and diameter of the resonance adjuster 41. In addition, the resonance level can be reduced by lowering the amplitude level of noise due to acoustic resonance.

（実施の形態３）
実施の形態３に係る膨張弁は、図３に示すように、実施の形態１における管状の共鳴調整器３１を共鳴器形状の容器からなる共鳴調整器４２としたものである。この共鳴調整器４２は、容積の閉じた空間室（消音室）４３とそれに連通する所定長さと所定断面積の連通路４４とからなる。この共鳴調整器４２を弁室１４の側方に連結することにより、共鳴空間の閉端が弁本体１の外側に取り付けられた共鳴調整器４２の閉鎖された側の端部４２ａとなる。実施の形態３に係る膨張弁は、共鳴器形状の容器からなる共鳴調整器４２を取り付けるものであるので、配管１９の共鳴特性を調整するとともに、低周波数の騒音レベルを低減させることができる。したがって、共鳴音の振幅レベルがより一層低減される。 (Embodiment 3)
As shown in FIG. 3, the expansion valve according to the third embodiment is such that the tubular resonance regulator 31 in the first embodiment is a resonance regulator 42 formed of a resonator-shaped container. The resonance adjuster 42 includes a space chamber (noise reduction chamber) 43 having a closed volume, a communication path 44 having a predetermined length and a predetermined cross-sectional area communicating with the space chamber. By connecting the resonance adjuster 42 to the side of the valve chamber 14, the closed end of the resonance space becomes the closed end 42 a of the resonance adjuster 42 attached to the outside of the valve body 1. Since the expansion valve according to the third embodiment is provided with the resonance adjuster 42 formed of a resonator-shaped container, the resonance characteristic of the pipe 19 can be adjusted and the noise level at a low frequency can be reduced. Therefore, the amplitude level of the resonance sound is further reduced.

（実施の形態４）
実施の形態４に係る膨張弁は、図４に示すように、実施の形態１における共鳴調整器３１の内部に音波を反射しにくい部材４５を取り付けたものであって、音波を反射しにくい部材４５としては、金属繊維、焼結合金などの多孔質材料からなるものを取り付けたものである。このような音波を反射しにくい部材共鳴調整器の内部に取り付けることにより、共鳴音の反射音を低減することができ、共鳴音の振幅レベルを低減して、騒音をより低減することができる。 (Embodiment 4)
As shown in FIG. 4, the expansion valve according to the fourth embodiment is a member in which a member 45 that hardly reflects sound waves is attached to the inside of the resonance regulator 31 according to the first embodiment, and is a member that hardly reflects sound waves. As for 45, what consists of porous materials, such as a metal fiber and a sintered alloy, is attached. By attaching such a sound wave to the inside of the member resonance adjuster that hardly reflects, the reflected sound of the resonance can be reduced, the amplitude level of the resonance can be reduced, and the noise can be further reduced.

（実施の形態５）
実施の形態５に係る膨張弁は、実施の形態４と同様に、実施の形態１における共鳴調整器３１の内部に音波を反射しにくい部材４６を取り付けたものである。この場合における音波を反射しにくい部材４６は、図５に示すように、ばね４６ａにより弾性的に支持された板材４６ｂを圧力変動に反応して変位させるものである。この場合も実施の形態４と同様に共鳴音の反射音を吸収することができ、共鳴音の振幅レベルを低減して、騒音をより低減することができる。 (Embodiment 5)
In the expansion valve according to the fifth embodiment, as in the fourth embodiment, a member 46 that hardly reflects sound waves is attached to the inside of the resonance regulator 31 in the first embodiment. In this case, as shown in FIG. 5, the member 46 that hardly reflects sound waves displaces the plate material 46b elastically supported by the spring 46a in response to pressure fluctuation. In this case as well, the reflected sound of the resonance can be absorbed as in the fourth embodiment, and the amplitude level of the resonance can be reduced to further reduce the noise.

（実施の形態６）
実施の形態１〜実施の形態５は、弁室１４の側面に接続される配管１９の共鳴特性を調整する共鳴調整器についてのものであったが、実施の形態６は、図６に示されるものであって、弁本体１の下面の配管接続部５１に接続される配管５２の共鳴モードの調整に関する。なお、この実施の形態における弁本体１下面の配管接続部５１は、実施の形態１の場合のような継手用配管が設けられていない。 (Embodiment 6)
The first to fifth embodiments are related to a resonance regulator that adjusts the resonance characteristics of the pipe 19 connected to the side surface of the valve chamber 14, but the sixth embodiment is shown in FIG. This relates to the adjustment of the resonance mode of the pipe 52 connected to the pipe connection portion 51 on the lower surface of the valve body 1. In this embodiment, the pipe connection portion 51 on the lower surface of the valve body 1 is not provided with a joint pipe as in the first embodiment.

実施の形態６では、実施の形態１〜５の場合のように、配管接続部５１に対向する面に共鳴調整器５３を取り付ける場所がない。また、絞り部１８との間に弁室１４もない。このために、弁座１３の下方部分に空間部５４を設けるとともに、空間部５４を外部に開口する開口部５５を空間部５４の側方に設け、さらに、この開口部５５の外側にソケット部５６を形成している。そして、このソケット部５６にろう付けにより同心状に共鳴調整器５３を取り付けたものである。   In the sixth embodiment, unlike the first to fifth embodiments, there is no place to attach the resonance adjuster 53 to the surface facing the pipe connecting portion 51. Further, there is no valve chamber 14 between the throttle portion 18. For this purpose, a space portion 54 is provided in a lower portion of the valve seat 13, and an opening portion 55 that opens the space portion 54 to the outside is provided on the side of the space portion 54. 56 is formed. The resonance adjuster 53 is concentrically attached to the socket portion 56 by brazing.

この場合の配管５２についての共鳴空間は、折れ曲がったような形態になる。そして、共鳴モードの節は、例えば大口径のフィルタ５７が取り付けられている場合は、その大口径部５７ａの位置となる。また、共鳴モードの閉端は、弁本体１の外側に取り付けられた共鳴調整器５３の閉鎖された側の端部５３ａとなる。このように共鳴特性が調整されることにより、絞り部１８で発生する加振エネルギは、共鳴モードの腹からずれた個所で加えられることになり、共鳴音の振幅を低減することができ、騒音を低下させることができる。   In this case, the resonance space for the pipe 52 is bent. The node of the resonance mode is, for example, the position of the large-diameter portion 57a when the large-diameter filter 57 is attached. The closed end of the resonance mode is an end portion 53a on the closed side of the resonance regulator 53 attached to the outside of the valve body 1. By adjusting the resonance characteristics in this way, the excitation energy generated in the throttle unit 18 is applied at a location deviated from the antinode of the resonance mode, and the amplitude of the resonance can be reduced. Can be reduced.

（実施の形態７）
実施の形態７に係る膨張弁は、実施の形態６の場合と同様に、弁本体１の下面の配管接続部６１に共鳴調整器６２を設けたものである。より具体的には、図７に示すように、配管接続部６１には実施の形態１のような継手用配管が設けられている。そして、配管接続部６１の継手用配管に配管内の空間を外部に開口する開口部６３が設けられている。さらに、開口部６３には継手用配管からバーリング部が膨出され、共鳴器形状の容器からなる共鳴調整器６２がこの開口部６３と同心状に配置されろう付けにより取り付けられている。なお、他の部分は、実施の形態１及び実施の形態６と同一であり、同一の要素には同一の符号を付し、その説明を省略する。 (Embodiment 7)
As in the case of the sixth embodiment, the expansion valve according to the seventh embodiment is provided with a resonance adjuster 62 in the pipe connecting portion 61 on the lower surface of the valve body 1. More specifically, as shown in FIG. 7, the pipe connection portion 61 is provided with a joint pipe as in the first embodiment. And the opening part 63 which opens the space in piping outside in the piping for joints of the piping connection part 61 is provided. Further, a burring portion is bulged from the joint pipe in the opening 63, and a resonance adjuster 62 made of a resonator-shaped container is disposed concentrically with the opening 63 and attached thereto by brazing. The other parts are the same as those in the first and sixth embodiments, and the same elements are denoted by the same reference numerals and the description thereof is omitted.

実施の形態７は、このように構成されているので、配管５２についての共鳴空間及び共鳴モードは、実施の形態６の場合と同様になり、実施の形態６の場合と同様の共鳴特性の調整が行われる。なお、共鳴モードの閉端は、弁本体１の外側に取り付けられた共鳴調整器６２の閉鎖された側の端部６２ａとなる。また、この場合は、共鳴器形状の容器からなる共鳴調整器６２が取り付けられているので、実施の形態７に係る膨張弁は、実施の形態６の膨張弁と同様の共鳴特性を調整するとともに、低周波数の騒音レベルを低減させることができる。   Since the seventh embodiment is configured as described above, the resonance space and the resonance mode for the pipe 52 are the same as those in the sixth embodiment, and the resonance characteristics are adjusted in the same manner as in the sixth embodiment. Is done. The closed end of the resonance mode is an end portion 62a on the closed side of the resonance adjuster 62 attached to the outside of the valve body 1. In this case, since the resonance adjuster 62 formed of a resonator-shaped container is attached, the expansion valve according to the seventh embodiment adjusts the resonance characteristics similar to those of the expansion valve according to the sixth embodiment. The noise level of low frequency can be reduced.

（変形例）
（１）各実施の形態において、共鳴調整器３１、４１、４２、５３、６２の開口部３０、５５、６３への取付は、開口部３０、５５、６３にソケット部３２、５６又はバーリング部を設け、このソケット部３２、５６又はバーリング部にろう付けしているが、ろう付けでなく溶接とすることも可能である。また、共鳴調整器３１、４１、４２、５３、６２のろう付けや溶接による弁本体１や弁駆動部２への熱影響が問題になる場合には、配管接続部１１、１２、５１、６１に継手用配管を設けているのと同様に、この開口部３０、５５、６３に短い配管を設けてもよい。この場合、共鳴調整器３１、４１、４２、５３、６２を取り付けない状態の膨張弁を完成品とする場合は、開口部３０、５５、６３に短い配管を設けた状態で出荷するようにすればよい。なお、共鳴調整器３１、４１、４２、５３、６２の開口部３０、５５、６３への取付は、漏れが生じず強度が問題にならないものであれば、上記のようなろう付けや溶接によらずにテーパねじによって取付することも可能である。 (Modification)
(1) In each embodiment, the resonance adjusters 31, 41, 42, 53, 62 are attached to the openings 30, 55, 63 by attaching the sockets 32, 56 or the burring portion to the openings 30, 55, 63. However, it is possible to use welding instead of brazing. Further, when the thermal influence on the valve main body 1 or the valve driving unit 2 due to brazing or welding of the resonance adjusters 31, 41, 42, 53, 62 becomes a problem, the pipe connecting portions 11, 12, 51, 61 are used. A short pipe may be provided in the openings 30, 55, and 63 in the same manner as the pipe for a joint is provided. In this case, when the expansion valve without the resonance adjusters 31, 41, 42, 53, 62 is made a finished product, it should be shipped with a short pipe provided in the openings 30, 55, 63. That's fine. Note that the resonance adjusters 31, 41, 42, 53, 62 can be attached to the openings 30, 55, 63 by brazing or welding as described above if leakage does not occur and strength does not matter. It is also possible to attach with a taper screw.

（２）各実施の形態においては、開口部３０、５５が１個しか明示されていないが、この開口部３０、５５を複数個設けるとともに、開口部３０、５５に連通する共鳴調整器３１、４１、４２、５３を複数個弁本体１の外側に取り付けるようにしてもよい。膨張弁に接続される略液冷媒で満たされる配管１９、５１には、フィルタ３５、５７だけではなく、各種機器が設けられるため、弁室１４部分を共鳴モードの腹とする複数の共鳴モードが形成されることがある。例えば、実施の形態１において、配管１９に大口径のフィルタ３５と受液器（図示せず）が直列に接続されているような場合、閉端を弁室１４とし、開放端をフィルタ３５とする共鳴空間と、閉端を弁室１４とし、開放端を受液器とする共鳴空間とが形成されることがあり得る。このような場合、例えば、複数の共鳴調整器３１を同一水平面上において、配管接続部１１の軸線に対しそれぞれ４５度傾けた位置の弁室１４の壁に二つの開口部３０を設け、二つの開口部３０に対し、前記二つの共鳴空間の共鳴特性に見合った共鳴調整器３１を分けて取り付ける。このようにすると、二つの共鳴調整器３１が個別に各共鳴空間による共鳴振幅の共鳴レベルを低減して騒音を低下させることができる。   (2) In each embodiment, only one opening 30 and 55 is clearly shown. However, a plurality of the openings 30 and 55 are provided, and the resonance regulator 31 communicating with the openings 30 and 55 is provided. A plurality of 41, 42, and 53 may be attached to the outside of the valve body 1. Since the pipes 19 and 51 that are filled with the substantially liquid refrigerant connected to the expansion valve are provided with various devices in addition to the filters 35 and 57, there are a plurality of resonance modes in which the valve chamber 14 portion is the antinode of the resonance mode. Sometimes formed. For example, in Embodiment 1, when a large-diameter filter 35 and a liquid receiver (not shown) are connected in series to the pipe 19, the closed end is the valve chamber 14, and the open end is the filter 35. And a resonant space having the closed end as the valve chamber 14 and the open end as the liquid receiver may be formed. In such a case, for example, two openings 30 are provided on the wall of the valve chamber 14 at a position inclined by 45 degrees with respect to the axis of the pipe connection portion 11 on the same horizontal plane, A resonance adjuster 31 corresponding to the resonance characteristics of the two resonance spaces is separately attached to the opening 30. In this way, the two resonance adjusters 31 can individually reduce the resonance level of the resonance amplitude by each resonance space to reduce noise.

（４）上記各実施の形態では、膨張弁について説明しているが、これら膨張弁は、家庭用空気調和機、店舗、オフィスビルなどの業務用エアコン、冷蔵庫、冷凍庫などあらゆる冷凍装置に使用することができ、これら装置における膨張弁の騒音を低減することができる。   (4) Although the expansion valves have been described in the above embodiments, these expansion valves are used for all refrigeration apparatuses such as domestic air conditioners, commercial air conditioners such as stores and office buildings, refrigerators, and freezers. The noise of the expansion valve in these devices can be reduced.

本発明の実施の形態１に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 1 of this invention. 本発明の実施の形態２に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 2 of this invention. 本発明の実施の形態３に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 3 of this invention. 本発明の実施の形態４に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 4 of this invention. 本発明の実施の形態５に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 5 of this invention. 本発明の実施の形態６に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 6 of this invention. 本発明の実施の形態７に係る膨張弁の縦断面図である。It is a longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 7 of this invention. マルチ型空気調和機の代表的冷媒回路図である。It is a typical refrigerant circuit diagram of a multi type air conditioner. 従来膨張弁に接続される液冷媒で満たされている配管の共鳴空間説明図である。It is resonance space explanatory drawing of piping filled with the liquid refrigerant connected to the conventional expansion valve. 配管における共鳴モード説明図である。It is resonance mode explanatory drawing in piping.

符号の説明Explanation of symbols

１…弁本体、１１、１２、５１、６１…配管接続部、１８…絞り部、１９、５２…配管３０、５５、６３…開口部、３１、４１、４２、５３、６２…共鳴調整器、４５、４６…（音波を反射しにくい）部材。   DESCRIPTION OF SYMBOLS 1 ... Valve body, 11, 12, 51, 61 ... Pipe connection part, 18 ... Restriction part, 19, 52 ... Pipe 30, 55, 63 ... Opening part, 31, 41, 42, 53, 62 ... Resonance regulator, 45, 46... (Members that hardly reflect sound waves)

Claims (8)

弁本体と、弁本体内部に形成される絞り部と、この絞り部の前後に連通する二つの配管接続部と、略液冷媒で満たされる配管が接続される配管接続部から絞り部に至る冷媒流通路を弁本体の外部に開放する少なくとも一つの開口部とを有し、前記弁本体は、略液冷媒で満たされる配管の共鳴特性を調整する共鳴空間を備えた共鳴調整器を、前記開口部に連通する態様で弁本体の外側に取り付け可能に形成されていることを特徴とする膨張弁。   Refrigerant from the valve body, the throttle formed inside the valve body, two pipe connecting parts communicating before and after the throttle part, and the pipe connecting part connected to the pipe substantially filled with liquid refrigerant to the throttle part At least one opening that opens the flow passage to the outside of the valve body, and the valve body includes a resonance regulator having a resonance space that adjusts resonance characteristics of a pipe that is substantially filled with liquid refrigerant. An expansion valve characterized by being formed so as to be attachable to the outside of the valve body in a mode communicating with the portion. 共鳴調整器が、前記開口部に連通する態様で弁本体の外側に取り付けられていることを特徴とする請求項１記載の膨張弁。   The expansion valve according to claim 1, wherein a resonance regulator is attached to the outside of the valve body in a manner communicating with the opening. 前記開口部は複数個設けられており、これら開口部に連通するように複数の共鳴調整器が弁本体の外側に取り付けられていることを特徴とする請求項１記載の膨張弁。   The expansion valve according to claim 1, wherein a plurality of the openings are provided, and a plurality of resonance adjusters are attached to the outside of the valve main body so as to communicate with the openings. 前記共鳴調整器は、管状容器であることを特徴とする請求項１〜３の何れか１項に記載の膨張弁。   The expansion valve according to claim 1, wherein the resonance adjuster is a tubular container. 前記共鳴調整器は、共鳴器形状の容器であることを特徴とする請求項１〜３の何れか１項に記載の膨張弁。   The expansion valve according to claim 1, wherein the resonance adjuster is a resonator-shaped container. 前記共鳴調整器は、内部に音波を反射しにくい部材が取り付けられていることを特徴とする請求項１〜５の何れか１項に記載の膨張弁。   The expansion valve according to any one of claims 1 to 5, wherein a member that hardly reflects sound waves is attached to the resonance adjuster. 前記音波を反射しにくい部材は、多孔質体からなることを特徴とする請求項６記載の膨張弁。   The expansion valve according to claim 6, wherein the member that hardly reflects sound waves is made of a porous body. 請求項１〜７の何れか１項に記載の膨張弁を用いたことを特徴とする空気調和機。   An air conditioner using the expansion valve according to any one of claims 1 to 7.
JP2006106975A 2006-04-07 2006-04-07 Expansion valve and air conditioner using the same Expired - Fee Related JP4079177B2 (en)

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JP2006106975A JP4079177B2 (en) 2006-04-07 2006-04-07 Expansion valve and air conditioner using the same
US12/224,889 US20090019871A1 (en) 2006-04-07 2007-04-09 Expansion Valve and Air Conditioner
AU2007236648A AU2007236648B2 (en) 2006-04-07 2007-04-09 Expansion valve and air conditioner
EP07741242A EP2006617A4 (en) 2006-04-07 2007-04-09 Expansion valve and air conditioner
CN2007800119165A CN101416006B (en) 2006-04-07 2007-04-09 Expansion valve and air conditioner
KR1020087022885A KR20080096838A (en) 2006-04-07 2007-04-09 Expansion valve and air conditioner
PCT/JP2007/057806 WO2007116991A1 (en) 2006-04-07 2007-04-09 Expansion valve and air conditioner

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EP2006617A4 (en) 2010-02-17
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CN101416006B (en) 2010-12-08
EP2006617A9 (en) 2009-07-29
KR20080096838A (en) 2008-11-03
WO2007116991A1 (en) 2007-10-18
EP2006617A2 (en) 2008-12-24
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AU2007236648B2 (en) 2010-05-13
CN101416006A (en) 2009-04-22

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